WO2005116492A1 - Joint etanche radial pour un arbre - Google Patents

Joint etanche radial pour un arbre Download PDF

Info

Publication number
WO2005116492A1
WO2005116492A1 PCT/EP2005/004531 EP2005004531W WO2005116492A1 WO 2005116492 A1 WO2005116492 A1 WO 2005116492A1 EP 2005004531 W EP2005004531 W EP 2005004531W WO 2005116492 A1 WO2005116492 A1 WO 2005116492A1
Authority
WO
WIPO (PCT)
Prior art keywords
radial shaft
sealing
sealing lip
shaft seal
seal according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2005/004531
Other languages
German (de)
English (en)
Spanish (es)
Inventor
Uwe Braun
Klaus Schäfer
Joachim Heinermann
Eberhard Bock
Armin Hintenlang
Kurt Eswald
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carl Freudenberg KG
Original Assignee
Carl Freudenberg KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carl Freudenberg KG filed Critical Carl Freudenberg KG
Publication of WO2005116492A1 publication Critical patent/WO2005116492A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
    • F16J15/326—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals with means for detecting or measuring relative rotation of the two elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips

Definitions

  • the invention relates to a radial shaft seal for a shaft guided through a housing wall, in particular in coolant pumps.
  • Coolant pumps use seals that prevent coolant from escaping along the shaft driving the impeller. Since coolant pumps are often used over a longer period of time, high demands are placed on such seals. State of the art
  • a radial shaft sealing system for a coolant pump has become known, in which two sealing lips are used, which are inclined against the pressure direction and which are held by membrane bodies. Support bodies are also used to support the sealing lips. The sealing lips themselves slide on a sleeve made of austenitic stainless steel and press-fitted onto the shaft.
  • the construction of this sealing system is very complex and is difficult to assemble.
  • the invention has for its object to provide a radial shaft seal that gives a good seal, can be easily manufactured and assembled.
  • a radial shaft seal of the type mentioned at the outset in that the seal consists of a stiffening body and vulcanized sealing element thereon and the sealing element has two sealing lips, one behind the other, directed towards the shaft and the interior to be sealed, one of which overlaps the inner one primary sealing lip is larger than the coverage of the outer secondary sealing lip.
  • the seal consists of a stiffening body and vulcanized sealing element thereon and the sealing element has two sealing lips, one behind the other, directed towards the shaft and the interior to be sealed, one of which overlaps the inner one primary sealing lip is larger than the coverage of the outer secondary sealing lip.
  • Mechanical seals have so far been used in water pumps which, due to their design, have a low level of leakage, which is regarded as a disadvantage. With these mechanical seals, the mechanical seal and the counter ring are supported on one another in a rotatable manner and under axial preload and are lubricated by the medium to be sealed. In many cases, a silicate-containing liquid is used as the coolant, which evaporates between the slide ring and the counter ring, the solid components being precipitated out.
  • Another disadvantage of mechanical seals is the price, the large installation space in the axial and radial directions and the difficult assembly, because mechanical seals consist of a large number of individual parts. The new seal provides a good seal, even at higher pressures, whereby the excess pressure can reach up to 5 bar. Negative pressures are also sealed, which can arise, for example, when coolant is drawn in to fill the cooling system.
  • the sealing element is formed from an elastomer which is vulcanized onto the stiffening body. Individual sealing parts are not available, but the stiffening body and sealing element form a unit.
  • the inner primary sealing lip is preferably made with a greater thickness than the outer secondary sealing lip.
  • the thickness of the primary sealing lip is set at 0.6 to 1.8 mm.
  • the thickness of the secondary sealing lip is adjusted accordingly and is between 0.4 and 1.7 mm.
  • the inward angle ⁇ at the sealing edges of the sealing lips is also chosen to be larger than the outward angle ß.
  • Favorable angular dimensions are ⁇ 30 ° to 60 ° for the internal angles and 20 ° to 40 ° for the external angles.
  • the inner lip diameter is chosen with reference to the outer shaft diameter and is slightly larger than the outer shaft diameter. This creates a sealing lip overlap that varies slightly depending on the medium to be sealed. In the present sealing element consisting of two sealing lips, care must be taken that the inner sealing lip has a greater overlap than the outer sealing lip. To support the seal, the space between the two sealing lips can be filled with lubricant.
  • the shaft is surrounded in the sealing area by a sleeve on which the sealing lips rest. It is advantageous if the running sleeve has a radially aligned collar on its inner edge facing the interior to be sealed. This collar is a kind of centrifugal disc that keeps contaminants away from the seal. If necessary, the centrifugal disc can be provided with swirl elements at its edge to support the centrifugal effect.
  • the barrel is provided with a flange on its inner edge facing towards the surroundings.
  • the barrel sleeve itself is made of a hard metal to counteract signs of wear.
  • FIG. 1 shows: the radial shaft seal enlarged in section;
  • Figure 2 shows the radial shaft seal in section placed on a shaft with a sleeve.
  • 3 the radial shaft seal with shaft inserted in a housing; 4a and 4b a barrel sleeve in section and in plan view with swirl elements; 5a and 5b show another embodiment of the running sleeve with swirl elements; 6: the seal in section with swirl elements attached to the primary sealing lip and
  • FIG. 7 a radial shaft seal with a support on PTFE attached to the primary sealing lip.
  • the sealing element 3 has two sealing lips 5 and 6 directed towards the interior 4 to be sealed, of which the inner primary sealing lip 5 has a greater overlap U than the outer secondary sealing lip 6.
  • the overlap UI of the primary sealing lip 5 results from DW-DPL: 2 and the overlap UA of the secondary sealing lip 6 results from (DW - DSL): 2, where DW is the shaft diameter and DPL and DSL are the respective inner diameters of the sealing lips after their manufacture.
  • the shaft 7 is shown in dashed lines.
  • the inner primary sealing lip 5 has a greater thickness T than the secondary sealing lip 6 whose thickness t is.
  • the stiffening body 2 is provided with the stop flange 8.
  • the sealing element 3 has an annular surface 9 with which it rests in a statically sealing manner at the edge of the housing opening.
  • the inner edge 10 of the stiffening body 2 lies approximately centrally between the two sealing lips 5 and 6.
  • FIG. 2 shows the seal 1 described in FIG. 1, placed on the shaft 7, the shaft 7 being surrounded by the running sleeve 12 in the sealing area.
  • a lubricant is filled in the space 13 between the sealing lips 5 and 6.
  • the angles of inclination ⁇ and ⁇ of the sealing lips 5 and 6 to the surface 14 of the shaft 6 are selected such that the sealing lips 5 and 6 bear against the shaft 7 in a manner that is neutral to the conveyance, so that the lubricant remains between the lips 5 and 6.
  • the funding-neutral design of the sealing lips takes place in that the angles ⁇ P of the primary lip and ⁇ s of the secondary sealing lip and the angles ßP of the primary lip and ßS of the secondary lip are identical. If the space 13 between the sealing lips 5 and 6 is not filled with the lubricant, on the other hand, it is favorable if, as shown in the figure, the angles ⁇ are larger than the angles ⁇ .
  • the running sleeve 12 is provided with a radially oriented collar 15 on its inner edge directed towards the interior 4 to be sealed. On the other side on the inner edge directed towards the surroundings 16 there is a flange 17. It goes without saying that the dimension of the sleeve 12 is also taken into account when dimensioning the shaft diameter DW for the overlap U.
  • FIG. 3 shows the seal 1, inserted into a bore 18 of a housing 19.
  • the seal 1 rests with the stop flange 8 on the stepped surface 20 of the bore 18.
  • the running sleeve 12 is firmly seated on the shaft 7, which in turn is mounted in the housing opening 18 via a ball bearing 21.
  • the space 13 is available for receiving lubricants.
  • 4a, 4b, 5a and 5b two different running sleeves 12 are shown in section and in plan view, which are each provided with the swirl elements 23 and 24 on their collars 15. The intersection lines are each indicated with a.
  • FIG. 6 shows an embodiment of the seal, in which the primary sealing lip 5 is provided with swirl elements 25 in a manner known per se. Leakage can be conveyed back into the space to be sealed by means of these swirl elements 25.
  • Fig. 7 shows an embodiment in which the primary sealing lip 5 is provided with a pad 30 made of a polytetrafluoroethylene (PTFE).
  • PTFE polytetrafluoroethylene
  • the thickness T of the primary sealing lip 5 is chosen to be 1.05 mm and the thickness t of the secondary sealing lip 6 is selected to be 0.6 mm.
  • the inner angle p of the primary sealing lip 5 is 34 ° and the inner angle ⁇ s of the secondary sealing lip 27.5 °.
  • the outer angle ßp of the primary sealing lip 5 is specified at 46 ° and the outer angle ß s of the secondary sealing lip 6 at 37.5 °.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

L'invention concerne un joint étanche radial pour un arbre pour un arbre dirigé à travers une révolution du logement, en particulier dans des pompes de refroidissement, ledit joint (1) étant composé d'un corps (2) de renforcement et d'un élément étanche vulcanisé, ce dernier présentant deux lèvres d'étanchéité (5, 6) placée l'une derrière l'autre, dirigées vers l'arbre (7) et vers la chambre interne (4) à étanchéifier, dans lesquelles le chevauchement (UI) de la première lèvre d'étanchéité (5) est plus important que le chevauchement (UA) de la seconde lèvre d'étanchéité (6) extérieure.
PCT/EP2005/004531 2004-05-19 2005-04-28 Joint etanche radial pour un arbre Ceased WO2005116492A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004025355.2 2004-05-19
DE200410025355 DE102004025355A1 (de) 2004-05-19 2004-05-19 Radialwellendichtung

Publications (1)

Publication Number Publication Date
WO2005116492A1 true WO2005116492A1 (fr) 2005-12-08

Family

ID=34972020

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/004531 Ceased WO2005116492A1 (fr) 2004-05-19 2005-04-28 Joint etanche radial pour un arbre

Country Status (2)

Country Link
DE (1) DE102004025355A1 (fr)
WO (1) WO2005116492A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1731804B1 (fr) * 2005-06-09 2008-08-13 Carl Freudenberg KG Joint d'étanchéité et assemblage comportant des lèvres d'étanchéité en série
ITMC20090138A1 (it) * 2009-06-10 2010-12-11 Umbra Meccanotecnica Kit monocomponente che integra una tenuta a labbro semplice o composta con il supporto di scivolo in modo non separabile.
EP2466172A1 (fr) * 2010-12-16 2012-06-20 Carl Freudenberg KG Bague d'étanchéité

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008010427B4 (de) * 2008-02-21 2010-05-12 Sartorius Stedim Biotech Gmbh Bioreaktor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0874770A1 (fr) * 1996-01-08 1998-11-04 Tils, Peter Procede d'emballage de produits congeles, de produits a jeter tells que des ordures menageres et analogues
DE10141138A1 (de) 2000-12-22 2002-07-04 Geraete & Pumpenbau Gmbh Kühlmittelpumpe mit Radialwellendichtsystem
US6428013B1 (en) * 1999-01-29 2002-08-06 Freudenberg-Nok General Partnership Reverse seal
WO2003069177A1 (fr) * 2002-02-14 2003-08-21 Nsk Ltd. Dispositif d'etancheite ainsi que roulement et unite de moyeu comprenant ce dispositif d'etancheite

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0614136Y2 (ja) * 1988-05-30 1994-04-13 エヌオーケー株式会社 密封装置
IT1319093B1 (it) * 2000-11-09 2003-09-23 Rft Spa Unita' di tenuta per organi meccanici relativamente rotanti,inparticolare per rulli di fonderia

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0874770A1 (fr) * 1996-01-08 1998-11-04 Tils, Peter Procede d'emballage de produits congeles, de produits a jeter tells que des ordures menageres et analogues
US6428013B1 (en) * 1999-01-29 2002-08-06 Freudenberg-Nok General Partnership Reverse seal
DE10141138A1 (de) 2000-12-22 2002-07-04 Geraete & Pumpenbau Gmbh Kühlmittelpumpe mit Radialwellendichtsystem
WO2003069177A1 (fr) * 2002-02-14 2003-08-21 Nsk Ltd. Dispositif d'etancheite ainsi que roulement et unite de moyeu comprenant ce dispositif d'etancheite
EP1475548A1 (fr) * 2002-02-14 2004-11-10 Nsk Ltd., Dispositif d'etancheite ainsi que roulement et unite de moyeu comprenant ce dispositif d'etancheite

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1731804B1 (fr) * 2005-06-09 2008-08-13 Carl Freudenberg KG Joint d'étanchéité et assemblage comportant des lèvres d'étanchéité en série
ITMC20090138A1 (it) * 2009-06-10 2010-12-11 Umbra Meccanotecnica Kit monocomponente che integra una tenuta a labbro semplice o composta con il supporto di scivolo in modo non separabile.
EP2466172A1 (fr) * 2010-12-16 2012-06-20 Carl Freudenberg KG Bague d'étanchéité
CN102537358A (zh) * 2010-12-16 2012-07-04 卡尔·弗罗伊登伯格公司 密封圈
CN102537358B (zh) * 2010-12-16 2015-09-16 卡尔·弗罗伊登伯格公司 密封圈
US9719597B2 (en) 2010-12-16 2017-08-01 Carl Freudenberg Kg Sealing ring

Also Published As

Publication number Publication date
DE102004025355A1 (de) 2006-02-02

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